U.S. patent number 6,886,424 [Application Number 10/603,855] was granted by the patent office on 2005-05-03 for layshaft automatic transmission having power-on shifting.
This patent grant is currently assigned to Ford Global Technologies, LLC. Invention is credited to Reid Alan Baldwin, David Allen Janson.
United States Patent |
6,886,424 |
Janson , et al. |
May 3, 2005 |
Layshaft automatic transmission having power-on shifting
Abstract
A power transmission for a motor vehicle includes an input, a
first layshaft, a second layshaft; a first power path for
transmitting power between the input and first layshaft, and
producing a first ratio of a speed of the first layshaft and a
corresponding speed of the input, a second power path for
transmitting power between the input and second layshaft, and
producing a second ratio of the speed of the second layshaft and
corresponding speed of the input; and a clutch for releasably
connecting the input and first power path.
Inventors: |
Janson; David Allen (Plymouth,
MI), Baldwin; Reid Alan (Howell, MI) |
Assignee: |
Ford Global Technologies, LLC
(Dearborn, MI)
|
Family
ID: |
33539816 |
Appl.
No.: |
10/603,855 |
Filed: |
June 25, 2003 |
Current U.S.
Class: |
74/329;
74/331 |
Current CPC
Class: |
F16H
3/006 (20130101); F16H 3/093 (20130101); F16H
61/682 (20130101); F16H 2003/007 (20130101); F16H
2061/0425 (20130101); F16H 2061/0429 (20130101); F16H
2200/0047 (20130101); Y10T 74/19223 (20150115); Y10T
74/19233 (20150115) |
Current International
Class: |
F16H
3/08 (20060101); F16H 3/00 (20060101); F16H
3/093 (20060101); F16H 003/08 () |
Field of
Search: |
;74/340,331,325,329,339 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Pang; Roger
Attorney, Agent or Firm: Kelly; Davis B.
Claims
We claim:
1. A multiple speed power transmission, particularly for motor
vehicles, comprising: an input; a first layshaft driveably
connectable through a first power to the input, and supporting a
first pinion thereon; a clutch for alternately connecting and
disconnecting the input and first layshaft; a first coupler for
releasably coupling the first pinion and first layshaft; a second
layshaft driveably connected through a second power path and a
one-way drive connection to the input, supporting a second pinion
thereon; a second coupler for selectively releasably coupling the
second pinion and second layshaft; and an output shaft supporting a
gear thereon, said gear being in meshing engagement with the first
pinion and second pinion.
2. The transmission of claim 1, wherein the first coupler and
second coupler are synchronizers.
3. The transmission of claim 1, wherein the first coupler is a
member of a group consisting of synchronizers and dog clutches.
4. The transmission of claim 1, wherein the second coupler is a
member of a group consisting of synchronizers and dog clutches.
5. The transmission of claim 1, wherein each of the first coupler
and second coupler is a member of a group consisting of
synchronizers and dog clutches.
6. The transmission of claim 1, wherein the one-way drive
connection is a member of the group consisting of a one-way clutch,
a sprag one-way clutch, a roller- one-way clutch, and a mechanical
diode.
7. The transmission of claim 1, wherein the clutch is a friction
clutch.
8. The transmission of claim 1, wherein: the first layshaft is
driveably connected to the input through the first power path
comprising a clutched input, a third pinion supported on the
clutched input, and a third gear supported on the first layshaft in
meshing engagement with said third pinion; and the second layshaft
is driveably connected to the input through the second power path
comprising a fourth pinion supported on the input, and a fourth
gear supported on the second layshaft in meshing engagement with
said fourth pinion.
9. The transmission of claim 1, wherein: the first layshaft is
driveably connected to the input through a first power path
comprising a third pinion supported on a clutched input, and a
third gear supported on the first layshaft in meshing engagement
with said third pinion; and the second layshaft is driveably
connected to the input through a second power path comprising a
fourth pinion supported on the input, a fourth gear supported on
the second layshaft in meshing engagement with said fourth
pinion.
10. The transmission of claim 8, wherein the first power path
produces a first speed ratio, and the second power path produces a
second speed ratio that is less than the first speed ratio.
11. The transmission of claim 9, wherein the first power path
produces a first speed ratio, and the second power path produces a
second speed ratio that is less than the first speed ratio.
12. The transmission of claim 8, wherein the first power path
produces a first ratio of the rotational speeds of the first
layshaft and input, and the second power path produces a second
ratio of the rotational speeds of the second layshaft and input
that is less than the first speed ratio.
13. The transmission of claim 9, wherein the first power path
produces a first ratio of the rotational speeds of the first
layshaft and input, and the second power path produces a second
ratio of the rotational speeds of the second layshaft and input
that is less than the first ratio.
14. A multiple speed ratio power transmission, particularly for
motor vehicles, comprising: an input; a first layshaft driveably
connectable through a first power path to the input, supporting a
first pinion and a first set of pinions thereon; a clutch for
alternately connecting and disconnecting the input and first
layshaft; a first coupler having a selectable coupling member
supported for movement on the first coupler, the first coupler
releasably coupling a pinion of the first pinion set and said first
layshaft in response to movement of the coupling member; a second
layshaft driveably connected through a second power path and a
one-way drive connection to the input, supporting a second pinion
and a second set of pinions thereon; a second coupler having a
selectable second coupling member supported for movement on the
second coupler, the second coupler releasably coupling a pinion of
the second pinion set and said second layshaft in response to
movement of the second coupling member; and an output supporting a
gear thereon, said gear being in meshing engagement with the first
pinion and second pinion, and further supporting a set of gears
thereon, each gear of said set of gears being in meshing engagement
with a pinion of the first pinion set and a pinion of the second
pinion set.
15. The transmission of claim 14, wherein the input is adapted for
connection to a power source, and the output is adapted for
connection to a load.
16. The transmission of claim 14, wherein: the first layshaft is
driveably connected to the input through a first power path
comprising an input shaft, a third pinion supported on the input
shaft, and a third gear supported on the first layshaft in meshing
engagement with said third pinion; and the second layshaft is
driveably connected to the input by a second power path comprising
a fourth pinion supported on the input, and a fourth gear supported
on the second layshaft in meshing engagement with said fourth
pinion.
17. The transmission of claim 14, wherein: the first layshaft is
driveably connected to the input through a first power path
comprising a third pinion supported on the input, and a third gear
supported on the first layshaft in meshing engagement with said
third pinion; and the second layshaft is driveably connected to the
input through a second power path comprising a fourth pinion
supported on the input, a fourth gear supported on the second
layshaft in meshing engagement with said fourth pinion.
18. The transmission of claim 16, wherein the first power path
produces a first speed ratio, and the second power path produces a
second speed ratio that is less than the first speed ratio.
19. The transmission of claim 17, wherein the first power path
produces a first speed ratio, and the second power path produces a
second speed ratio that is less than the first speed ratio.
20. The transmission of claim 16, wherein the first power path
produces a first ratio of the rotational speeds of the first
layshaft and input shaft, and the second power path produces a
second ratio of the rotational speeds of the second layshaft and
input that is less than the first speed ratio.
21. The transmission of claim 17, wherein the first power path
produces a first ratio of the rotational speeds of the first
layshaft and input, and the second power path produces a second
ratio of the rotational speeds of the second layshaft and input
that is less than the first speed ratio.
22. The transmission of claim 14, further comprising: primary
pinion-gear pairs, the pinions of said primary pairs being
supported on, and spaced mutually along the first layshaft, the
gears of said primary pairs being in engagement with the pinions of
said primary pairs, supported on, and spaced mutually along the
output; and primary couplers connected to the first layshaft, each
primary coupler having a selectable coupling member supported for
movement on the corresponding primary coupler, for releasably
coupling a pinion of the primary pinion-gear pairs and said first
layshaft in response to movement of said coupling member.
23. The transmission of claim 22, further comprising: secondary
pinions supported on, and spaced mutually along the second
layshaft, each secondary pinion being engaged with a gear of a
primary pinion-gear pair; and secondary couplers connected to the
second layshaft, each secondary coupler having a selectable
coupling member supported for movement on a corresponding secondary
coupler for releasably coupling a secondary pinion and said second
layshaft in response to movement of said coupling member.
24. The transmission of claim 22, further comprising: a reverse
pinion supported on the first layshaft; a reverse gear supported on
the output; and a reverse idler engaged with the reverse pinion and
reverse gear, and wherein a primary coupler driveably connects the
reverse pinion and the first layshaft.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
This invention pertains to the field of automatic shift manual
transmissions and select shift manual transmissions, particularly
to the types of these transmissions applicable to motor
vehicles.
2. Description of the Prior Art
Automatic transmissions for transmitting power between an input and
an output, either over a continuously variable range of speed
ratios or in discrete step changes among speed ratios, have
associated with them several sources of parasitic losses, which
adversely affect fuel economy. These losses are associated with a
torque converter, open hydraulic friction clutches and brakes,
hydraulic pump, and gear meshes.
To improve fuel economy in a motor vehicle having an automatic
transmission, an automated shift manual (ASM) transmission can be
used to eliminate or substantially reduce all of these parasitic
losses except gear mesh losses. An ASM transmission generally
performs gear ratio changes by first interrupting torque
transmitted from the engine to the transmission input, preparing
the transmission components associated with the next speed ratio,
and then restoring torque. A primary functional feature of ASM
transmissions is the need to interrupt power transmitted from the
engine to the transmission input shaft before or during each gear
ratio change. This requirement can result in low quality gear ratio
changes, which a vehicle operator or passenger may sense as noise,
vibration and harshness.
A transmission operating in accordance with the present invention
avoids entirely any interruption of power during gear ratio changes
and avoids the inherent shift quality problems of ASMS. This
invention, however, also reduces the magnitude of parasitic losses
inherent in the operation of an automatic transmission to a much
lower magnitude than is present in a conventional ASM
transmission.
SUMMARY OF THE INVENTION
A transmission according to the present invention includes only one
friction clutch for releasably connecting a source of power, such
as an engine or motor, and a transmission input. Gear ratio changes
are accomplished through the use of couplers, such as synchronizers
or dog clutches, which mutually driveably connect components
operative in each speed ratio, which couplers produce very little
drag loss when engaged, and do not require a continuous supply of
power to stay engaged.
Power interruption during shifting is avoided by providing
alternate torque or power paths, which transmit power between a
transmission input and the output during a gear ratio change. A
secondary power path bypasses the friction clutch, but contains a
one-way clutch. Before starting an upshift from an initial gear to
a higher gear, one power path is set for a slightly lower speed
ratio than the initial gear by engaging synchronizers or dog
clutches, thereby causing the one-way clutch to overrun. In order
to transfer power to the second torque path, the friction clutch is
released and the secondary power path carries torque through the
one-way clutch. Transfer of torque to the secondary power path is
essentially a downshift to a speed ratio that is slightly lower
than the current or off-going gear ratio.
While the secondary power path carries torque, the main or primary
power path is set similarly for the destination gear of the
gearshift by engaging synchronizers or dog clutches. When the
friction clutch is re-engaged, torque is transferred back to the
primary torque path causing the one-way clutch to overrun again.
Downshifts are accomplished by reversing this sequence of
steps.
All the gear ratio changes including the acceleration of the
vehicle from a stop or idle condition, usually referred to as
launch, use the same friction clutch. The only additional hardware
required is a one-way clutch, the gearing, and a coupler on a
second layshaft associated with the secondary torque path.
The principle of the present invention can be applied to all of the
up-shifts of a particular transmission or any number of the
up-shifts depending upon the number of secondary torque paths that
are provided.
In realizing these advantages, a power transmission for a motor
vehicle includes an input; a first layshaft driveably, supporting a
first pinion thereon; a clutch for alternately connecting and
disconnecting the input and first layshaft; a first coupler for
releasably coupling the first pinion and first layshaft; a second
layshaft driveably connected through a one-way drive connection to
the input, supporting a second pinion thereon; a second coupler for
selectively releasably coupling the second pinion and second
layshaft; and an output shaft supporting a gear thereon, said gear
being in meshing engagement with the first pinion and second
pinion.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a schematic diagram showing the gear arrangement of the
transmission according to the present invention.
FIG. 2 is a chart containing an example of the number of teeth for
each of the gears and pinions shown in FIG. 1.
FIG. 3 is a chart that indicates the state of engagement of a
friction clutch and the couplers corresponding to the steps for
producing gear ratio changes in a transmission according to the
present invention.
FIG. 4 is a chart that shows an example of the resulting speed
ratios for various paths and components, a torque ratio and the
gear ratio steps corresponding to various operating steps of the
chart of FIG. 3.
FIG. 5 is a schematic diagram showing another arrangement of the
power path in which the input clutch is located on the first
layshaft.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to FIG. 1 a transmission according to the present
invention includes an input 10 adapted to driveably connect a power
source, such as an internal combustion engine or electric motor,
and an output 12 for driving a load, such as the driven wheels of a
motor vehicle connected through a powertrain that may include a
drive shaft, differential mechanism, and axle shafts.
A primary layshaft 14 and secondary layshaft 16, arranged
substantially parallel to the output 12, each support pinions that
are in continually meshing engagement with gears supported
rotatably on the output 12.
A clutched input 18, preferably substantially aligned with output
12, is releasably connected to input 10 through a friction clutch
22, whose output element 20 frictionally engages the clutch's input
element 24, which is drivably connected to input 10.
A pinion 26, journalled on member 24 and connected to input 10, is
engaged with a gear 28, which is journalled on secondary layshaft
16. A one-way clutch 30, also supported rotatably on layshaft 16,
has an inner race 32 fixed to layshaft 16 and an outer race 34
drivably connected to gear 28.
Clutched input 18 supports a pinion 36, which is in continual
meshing engagement with gear 38, supported rotatably on primary
layshaft 14.
In this way, a primary power path, having a speed ratio that is
approximately 0.711 when pinion 36 and gear 38 have the number of
teeth specified in FIG. 2, is established between input 10 and
layshaft 14. When clutch 22 is engaged, the primary power path
causes the speed of layshaft 14 to be approximately 0.711 times the
speed of input 10. A secondary power path, having a speed ratio of
approximately 0.703 when pinion 26 and gear 28 have the number of
teeth specified in FIG. 2, is established between layshaft 16 and
input 10. Clutch 30 drivable connects gear 28 and layshaft 16 when
input 10 drives layshaft 16, and clutch 30 overruns when the speed
of layshaft 16 exceeds the speed of gear 28. When clutch 30 is
driving, the secondary power path causes the speed of layshaft 16
to be approximately 0.703 times the speed of input 10.
Spaced axially along output 12 are gear elements of pinion-gear
pairs, each member of a pair in continuous meshing engagement with
the other member of the pair, and each pair being associated with a
particular speed ratio. For example, pinion 40, which is journalled
on layshaft 14, is in continuous meshing engagement with gear 42,
which is rotatably supported on output 12. Pinion 40 and gear 42
are associated with the third forward speed ratio. Pinion 44,
journalled on layshaft 14, is in continuous meshing engagement with
gear 46, which is rotatably supported on output 12. Pinion 44 and
gear 46 are associated with the fourth forward speed ratio. Pinion
48, journalled on layshaft 14, is in continuous meshing engagement
with gear 50, which is rotatably supported on output 12. Pinion 48
and gear 50 are associated with the fifth forward gear ratio.
Reverse pinion 52, journalled on layshaft 14, is in continuous
meshing engagement with reverse idler 54, which is supported
rotatably on an idler shaft 55. Reverse output gear 56, which is
rotatably supported on output 12, is in continuous meshing
engagement with reverse idler 54. Pinion 52, idler 54 and gear 56
are associated with the reverse gear ratio.
Also spaced along the axis of output 12 are triplets comprising two
pinions, one of each pinion being supported on layshaft 14 and the
other on layshaft 16, and a gear supported on and fixed to output
12. For example, pinion 58, which is journalled on layshaft 14, is
in continuous meshing engagement with gear 60, supported on output
12. Pinion 62, which is journalled on layshaft 16, is also in
continuous meshing engagement with gear 60. Pinion 58, gear 60 and
pinion 62 form a triplet that is associated with the first forward
gear ratio.
Pinion 64, journalled on layshaft 14, is in continuous meshing
engagement with gear 66, supported on output 12. Pinion 68, which
is journalled on layshaft 16, is in continuous meshing engagement
with output gear 66. Pinion 64, gear 66 and pinion 68 form a
triplet that is associated with the second forward gear ratio.
Couplers 70, 82, 84 and 86, are preferably synchronizers of the
type used in manual automotive transmissions to connect releasably
a gear or pinion to a shaft after first synchronizing the speed of
the shaft and that of the pinion or gear. A coupler may also be
disengaged from any pinion or gear. An example of such a
synchronizer is disclosed in U.S. Pat. No. 4,222,281. Alternatively
the couplers may be a toothed clutch having dogteeth that are
engaged with clutch teeth on a gear or pinion. This invention may
use couplers in any combination of synchronizers and dog
clutches.
Each coupler, for example coupler 70, is fixed by a hub 72 on a
layshaft 14 for rotation at the speed of that layshaft. In the case
where a coupler is a synchronizer, it will be provided with a
conical surface 74, 76, which engages mutually with a corresponding
conical surface 78, 80, respectively, on the pinions located
adjacent the synchronizer. When these conical surfaces are forced
together into frictional contact, that engagement synchronizes the
speed of layshaft 14 to that of the pinion being engaged and
drivably connected through the synchronizer to layshaft 14.
Generally the synchronizer is equipped with a sleeve 81 supported
on the hub 72 for sliding movement leftward and rightward into
engagement with dogteeth carried on the pinion. When the dogteeth
of the sleeve engage those of the pinion, the pinion is connected
to the layshaft.
The hubs of couplers 82, 84 are rotatably secured to layshaft 14;
the hub 88 of coupler 86 is rotatably secured to layshaft 16.
In the case where the coupler 70 is a clutch, movement of the
sleeve 81 causes mutual engagement of dog teeth formed on the
sleeve and dog teeth carried on the pinions so that a drive
connection is made between the pinion and the layshaft, but without
first synchronizing the speed of the layshaft and the pinion.
A coupler 82, located between pinions 40 and 44, releasably
connects alternately those pinions and layshaft 14, and coupler 82
may be disengaged from both pinions. Coupler 84, located between
pinions 48 and 52, selectively, alternately produces a drive
connection between layshaft 14 and the selected pinion, and coupler
84 may be disengaged from both pinions. Another coupler 86 includes
a hub 88 driveably connected and supported for rotation on the
secondary layshaft 16. Coupler 86 is located between pinions 62 and
68 in order to selectively produce a drive connection between
layshaft 16 and those pinions.
In FIG. 1 the couplers 70, 82, 84, 86 are shown in a neutral
position, between the left-hand and right-hand extremities of
travel of the connecting element or sleeve, whose engagement with
the dog teeth carried on the pinions completes the drive connection
of the pinion and associated layshaft.
Referring now to FIG. 3, operation of the transmission will be
discussed with reference to the positional states of the couplers
and the applied or released condition of clutch 22. The
transmission is prepared for forward acceleration of the vehicle
from rest in the first gear ratio when the engagement sleeve 81 of
coupler 70 is moved leftward, the other couplers 82, 84 and 86 are
in the neutral position, and clutch 22 is disengaged. The power
source continually drives input 10 and pinion 26 at the speed of
the power source; gear 28 is driven by pinion 26 at the speed ratio
of the secondary power path, i.e., 0.703 times the speed of input
10, provided the gears and pinions have the sizes of the example of
FIG. 2. However, since coupler 86 is in the neutral position, no
power is transferred to output 12, and the speed of output 12 is
zero. Next, clutch 22 is applied, either manually by the vehicle
operator's manipulation of a clutch pedal, lever or button, or
automatically in response to a signal produced by a transmission
electronic control system. When clutch 22 is engaged, primary
layshaft 14 is driven through clutch 22, input 18, pinion 36, and
gear 38 at the speed ratio of the primary power path, i.e., 0.711
times the speed of input 10. Output 12 is driven from layshaft 14
through coupler 70, pinion 58 and gear 60, which is drivably fixed
to output 12. These actions complete the engagement of the first
forward speed ratio, whereby the output 12 is driven at a speed
ratio of 0.314.
An upshift from the first to the second speed ratio is accomplished
in a series of steps that begins by moving the engagement element
or sleeve of coupler 86 leftward to drivably connect pinion 62 and
the secondary layshaft 16. This action causes one-way clutch 30 to
overrun or permits it to continue to overrun. Then clutch 22 is
released, thereby causing one-way clutch 30 to driveably connect
layshaft 16 and gear 28, which drives output 12 through gear 60 at
a speed ratio of 0.310, a slight downshift from the first gear
ratio, 0.314. Next, the engagement element or sleeve of coupler 70
is moved from the left-hand to the right-hand position, thereby
drivably connecting pinion 64 and layshaft 14. Output 12 remains
driven through the secondary power path at a speed ratio of 0.310.
Clutch 22 is then applied, causing one-way clutch 30 to overrun,
and driving output 12 through the primary power path: pinion 36,
gear 38 and layshaft 14, which drives second speed pinion 64 and
second speed gear 66. Moving the sleeve of coupler 86 to the
neutral position, i.e., out of engagement with pinion 62 completes
the upshift to the second speed ratio from the first speed ratio.
Output 12 is driven at a speed ratio of 0.548.
The torque delivery path in the second forward speed ratio includes
input 10, clutch 22, input 18, gear 36, pinion 38, layshaft 14,
coupler 70, pinion 64, gear 66, and output 12.
An upshift from a second speed ratio to the third speed ratio is
similarly accomplished in a series of steps that begins by moving
the selection sleeve of coupler 86 to the right-hand position from
the neutral position, thereby driveably connecting pinion 68, gear
66, and output 12 through coupler 86, and layshaft 16. With the
transmission components so disposed, one-way clutch 30 overruns,
and the output remains driven through the primary power path at the
0.548 speed ratio. Then clutch 22 is released, which causes clutch
30 to produce a drive connection between layshaft 16 and gear 28.
The output 12 is driven through the secondary power path, pinion 68
and gear 66 at a slightly reduced speed ratio of 0.542. Next, the
selector sleeve of coupler 70 is moved to the neutral position and
the selector sleeve of coupler 82 is moved to the left-hand
position, thereby drivably connecting layshaft 14 and pinion 40.
The output remains driven through the secondary power path at the
0.542 speed ratio. Then clutch 22 is reapplied, which action causes
one-way clutch 30 to overrun and output 12 to be driven again
through the primary power path, pinion 40 and gear 42 at the third
forward speed ratio, 0.809. Finally the upshift to the third speed
ratio is completed by disengaging the secondary torque delivery
path upon moving the selector element 88 of coupler 86 to the
neutral position.
In the speed ratio changes described, only speed ratio changes to
the second and third forward speed ratios involve transmitting
power through the secondary power path, i.e., without interrupting
power flow between the engine and the transmission. However, any
number of the gear ratio changes could employ the secondary torque
delivery path to avoid power interruption, provided a pinion
corresponding to each of such speed ratios is supported on layshaft
16 and meshes with the output gear of the corresponding gear ratio.
Speed ratio changes to the fourth and fifth speeds involve
interrupting power flow from the engine to the transmission by
disengaging clutch 22.
An upshift from the third to the fourth forward speed ratio begins
with the step of disengaging clutch 22. Clutch 30 is inoperative
during engagement of the third and fourth forward gears and reverse
gear. Next, the selection element or sleeve of coupler 82 is moved
to the right-hand position, thereby driveably connecting layshaft
14 and pinion 44. Finally re-engaging clutch 22 complete the fourth
forward speed ratio. The torque delivery path for the fourth speed
ratio includes input 10, clutch 22, input 18, pinion 36, gear 38,
layshaft 14, coupler 82, pinion 44, gear 46, and output 12. The
fourth speed ratio is 1.052. Similarly an upshift from the fourth
to the fifth forward speed ratio begins by disengaging clutch 22.
Next, the selector element of coupler 82 is moved from the
right-hand position to the neutral position, and the selector
element of coupler 84 is moved from the neutral position to the
left-hand position, thereby driveably connecting layshaft 14 and
pinion 48. Re-engaging clutch 22 complete the upshift to the fifth
forward speed ratio. The torque delivery path for the fifth forward
speed ratio includes input 10, clutch 22, input 18, pinion 36, gear
38, layshaft 14, coupler 84, pinion 48, gear 50, and output 12. The
fifth speed ratio is 1.267.
Reverse drive is produced when the selector elements of couplers
70, 82, and 86 are in the neutral position and the selector element
of coupler 84 is moved to the right-hand position, thereby
driveably connecting pinion 52 and layshaft 14. Reverse idler 54,
which is rotatably supported on idler shaft 55, reverses the
direction of rotation so that gear 56 and the output 12 turn in the
opposite direction of rotation from the direction the forward drive
gear ratios. Reapplying clutch 22 completes the reverse drive
torque delivery path. The torque delivery path for reverse drive
includes input 10, clutch 22 shaft 18, pinion 36, gear 38, layshaft
14, coupler 84, pinion 52, reverse idler 54, gear 56, and output
12. The reverse drive speed ratio is -0.314.
The example set out in FIG. 4 was selected to produce the gear
ratios that would result from the transmission embodiment of FIG. 1
and using the gear and pinion sizes of FIG. 2.
The one-way clutch 30 represents a one-way drive connection through
which the input is connected to the second layshaft, and may be any
of the following: a one-way clutch, a sprag-type one-way clutch, a
roller-type one-way clutch, a mechanical diode of the type
described in U.S. Pat. Nos. 5,070,978; 5,597,057 and 6,065,576.
Referring now to the alternate embodiment of FIG. 5, an input 10'
supports and is driveably connected to both a pinion 26' of the
second power path, and a pinion 36 of the first power path. Pinion
26' is engaged with gear 28, which is supported on the second
layshaft; pinion 36 is engaged with gear 38', which is journalled
on the first layshaft 14' and is driveably connected to a clutch
22'. Gear 28 is connected through a one-way drive connection 30, to
second layshaft 16.
Preferably clutch 22' is a multiple plate friction clutch, and may
have a housing 24' connected to gear 38', and a disc 20' carried on
layshaft 14'. The disc moves alternately into frictional engagement
with housing 24' to connect gear 38' and layshaft 14' when the
clutch is applied, and out of engagement with the housing to
disconnect gear 38' and layshaft 14' when the clutch is
released.
An ASM transmission operating in accordance with the present
invention avoids entirely any interruption of power during gear
ratio changes and avoids the inherent shift control difficulties of
ASMs. This invention, however, also reduces the magnitude of
parasitic losses inherent in the operation of an automatic
transmission to a much lower magnitude than the losses associated
with a conventional ASM transmission.
Although the form of the invention shown and described here
constitutes the preferred embodiment of the invention, it is not
intended to illustrate all possible forms of the invention. Words
used here are words of description rather than of limitation.
Various changes in the form of the invention may be made without
departing from the spirit and scope of the invention as
disclosed.
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